US3827338A - Fluid device - Google Patents

Fluid device Download PDF

Info

Publication number
US3827338A
US3827338A US00174097A US17409771A US3827338A US 3827338 A US3827338 A US 3827338A US 00174097 A US00174097 A US 00174097A US 17409771 A US17409771 A US 17409771A US 3827338 A US3827338 A US 3827338A
Authority
US
United States
Prior art keywords
pinion
pistons
piston
casing
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US00174097A
Other languages
English (en)
Inventor
H Oguni
M Nakagawa
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kawasaki Heavy Industries Ltd
Kawasaki Motors Ltd
Original Assignee
Kawasaki Heavy Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kawasaki Heavy Industries Ltd filed Critical Kawasaki Heavy Industries Ltd
Application granted granted Critical
Publication of US3827338A publication Critical patent/US3827338A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F01B1/0641—Details, component parts specially adapted for such machines
    • F01B1/0668—Supporting and guiding means for the piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F01B1/0641—Details, component parts specially adapted for such machines
    • F01B1/0648—Cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
    • F01B13/061—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders
    • F01B13/063—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders with two or more series radial piston-cylinder units
    • F01B13/065—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders with two or more series radial piston-cylinder units directly located side by side

Definitions

  • ABSTRACT 183488; 123/44 This invention relates to fluid devices of the radial piston type providing eccentric rollers, eccentric pinions [56] References Cited or cams of elliptic or any shape as desired which are mounted on the piston pins for increasing the number UNITED STATES PATENTS of piston strokes and producing a high output power 593,470 11/1897 Heaton 123/44 B with mall capacity,
  • This invention relates to fluid devices, and more particularly it is concerned with a fluid pump or fluid motor of the radial piston type.
  • the invention obviates the aforementioned disadvantages of conventional fluid pumps or motors.
  • the invention has as its object the provision of a fluid pump or motor which is simple in construction, easy to make and adapted for operation under high pressure and/or at high speed.
  • the aforementioned object of this invention is accomplished by providing eccentric rollers, eccentric pinions or cams of elliptic or any other shape as desired which are mounted on the piston pins.
  • FIG. 1 is a sectional side view of the device according to this invention.
  • FIG. 2 is a fragmentary sectional front view of the device of FIG. 1;
  • FIG. 3 is a fragmentary enlarged view of FIG. 1;
  • FIG. 4 is a fragmentary enlarged view of FIG. 2;
  • FIG. 5 is a fragmentary sectional side view of another embodiment of this invention.
  • FIG. 6 to FIG. 8 are views in explanation of variations in the torque produced by the pistons
  • FIG. 9 is a diagrammatic representation of variations in a piston stroke in a conventional device.
  • FIG. 10 is a diagrammatic representation of one example of the piston stroke according to this invention.
  • FIG. 11 is an enlarged elevational view of one embodiment of the cam and ring rest
  • FIG. 12 is an elevational view of another embodiment of the cam and the ring rest
  • FIG. 13 is a cross sectional view similar to FIG. 3 illustrating another embodiment of the invention.
  • FIG. 14 is a cross sectional view of a further embodiment of the present invention.
  • FIG. 15 is a side view of the embodiment illustrated in FIG. 14.
  • a main shaft 1 is connected to a cylinder body 2 and held against rotation relative to the cylinder body by means of a spline 25.
  • a number of pistons 3 are fitted in the cylinder body 2 and arranged radially thereof.
  • a pair of pistons 3 disposed in 'side-by-side relation are connected to a piston pin 8 formed integrally with a pinion shaft 4.
  • the pinion shaft 4 has an axis 4 which is eccentric with respect to the axis 8 of the piston pin 8 (See FIG. 4).
  • a pinion 5 is mounted on each pinion shaft 4. The pinions 5 are maintained in meshing engagement with an internally toothed gear 9 which is secured to a case.
  • a plurality of cams 6 (which are in the form of rings in this embodiment) are each disposed on opposite sides of the pinion 5 (See FIG. 3) and each mounted on the outer peripheral surface of each pinion shaft 4.
  • the cams 6 are adapted to move in rolling motion on the inner peripheral surfaces of ring rests 7 mounted on opposite sides of the teeth of the internally toothed gear 9.
  • a rear cover 10 and a front cover 11 are clamped to opposite side portions of the internally toothed gear 9.
  • the main shaft 1 is journalled by bearings 26 and 12 mounted on the rear cover 10 and front cover 11 respectively.
  • a portion of the front cover 11 through which the main shaft I extends is sealed by an oil seal 13.
  • the rear cover 10 is formed with working fluid outlet and inlet ports 23 and 24. Whether these ports serve as outlet ports or inlet ports may vary depending on whether the device is used as a pump or a motor.
  • the rear cover 10 is further formed with annular fluid passageways 21 and 22 maintained in communication with the outlet and inlet ports 23 and 24 respectively, and fluid passageways 21' and 22' branching off from such annular fluid passageways 21 and 22 respectively.
  • a number of cylinder fluid chambers 18 each containing a quantity of fluid acting on the pistons 3 are formed in the cylinder body 2.
  • a number of fluid passageways l7 and 17' extending from the cylinder chambers 18 along the axis of the main shaft 1 to open in opposite side portions of the cylinder body 2 and a number of fluid passageways 19 each connecting a pair of cylinder chambers 18 disposed in side-byside relationship are also formed in the cylinder body 2.
  • valve plate 14 Interposed between the cylinder body 2 and rear cover 10 is a valve plate 14 which is formed with ducts 15 and 16, the ducts 15 being maintained in communication with the fluid passageways 21' formed in the rear cover 10 and the fluid passageways 17 formed in the cylinder body 2 and the ducts 16 being maintained in communication with the fluid passagway 22' formed in the rear cover 10 and the fluid passageways 17 formed in the cylinder body 2.
  • an oil pocket 20 Formed in the front cover 11 is an oil pocket 20 which is maintained in communication with the fluid passageways 17 formed in the cylinder body 2.
  • FIG. shows another embodiment of this invention in which a number of pistons 29 are mounted in a cylinder body 28 and arranged radially thereof.
  • Each of the pistons 29 is connected to a piston pin 30 which is formed integrally with a plurality of pinion shafts 31 disposed on opposite sides of the piston pin 30.
  • Each piston pin 30 is eccentric with respect to the associated pinion shafts 31.
  • a plurality of rings 33 are mounted on the pinion shafts 31 through bearings 33.
  • the rings 33 are adapted to move in rolling motion along the inner surfaces of ring rests 34 attached to a cover 35.
  • External gears 36 whose central axial line is aligned with the axis of the main shaft 1 are formed integrally with the cover 35 and disposed in the inwardly projecting portion thereof.
  • the pinions 32 are maintained in meshing engagement with the external gears 36.
  • a working fluid is supplied through the inlet port 23 and passes through the annular fluid passageway 21 and fluid passageway 21 to reach one of the ducts in the valve plate 14, thence is passes through one of the fluid passageways 17 in the cylinder body 2 to flow into one of the cylinder fluid chambers 18 to actuates one of the pistons 3.
  • part of the fluid passes through one of the fluid passages 19 to the cylinder fluid chamber 18 disposed in side-by-side relation with the first-mentioned cylinder fluid chamber 18 so as to actuate the adjacent piston 3.
  • Part of the fluid further passes through one of the fluid passageways 17 into the annular channel 20.
  • Thedevice according to this invention is designed such that the pressure of a quantity of fluid introduced into the oil pockets and the pressure of a quantity of fluid in the ducts 15 balance so as to preclude axial movement of the cylinder body 2.
  • Rolling movement or rotation of the pinion 5 on its own axis causes the associated pair of pistons 3 to move in reciprocating motion in the cylinder body 2 which in turn is caused to rotate relative to the internally toothed gear 9.
  • a path of movement of the axis 8 of a given piston pin 8 can be expressed as a curve 27 shown in FIG. 2. If the internally toothed gear 9 is firmly fixed, rotation of the pinions 5 on their own axis will cause the cylinder body 2 to rotate about the main shaft 1, thereby causing the main shaft 1 to rotate through the spline 25. Thus, the main shaft 1 functions as an output shaft.
  • FIG. 2 illustrating the relationship between adjacent pinion shafts 4 as the fluid device operates.
  • the pistons 3 effect a radially directed, relative to main shaft 1, reciprocating movement, however, the location of the pinion shaft 4 attached to each pair of pistons 3 is not always in direct radial alignment with the piston.
  • FIG. 2 illustrates the arrangement of the pistons 3 in a somewhat clock-like arrangement
  • the uppermost piston is the [2 oclock position and the lowermost piston is in the 6 oclock position with the four pistons between them being located in the 7 oclock, 8 oclock, 10 oclock, and 1] oclock positions.
  • the pistons 3 in the 12 oclock and 6 oclock positions have the axis of the pinion shaft in alignment with the axis of the corresponding piston, however, the four other pistons between the 6 oclock and 12 oclock positions have the axis of the pinion shaft displaced on one side or the other of the radially extending axis of the piston.
  • the spacing between the axes of the pinion shafts is a variable between the 12 oclock and 6 oclock positions.
  • the maximum spacing appears to be between the pinion shafts in the 12 o clock-ll oclock and 6 oclock-7 oclock positions.
  • the spacing between the l 1 oclock and 10 oclock positions and the 7 oclock and 8 oclock positions of the pinion shafts are considerably less due to the position of the piston pins 8.
  • each pinion 5 and cam 6 is swingably supported by the piston pin 8 mounted on each piston 3, bearings supporting the pinion shaft are unnecessary and the portion of the piston supporting the piston pin can be made compact. Accordingly, the space between the cylinder body and the case containing the gear 9 can be reduced with the pump being made more compact.
  • each piston 3 will move in reciprocating motion m times for each one complete revolution of the main shaft 1, so that the volume of operation fluid of the fluid motor for each revolution of the main shaft can be greatly increased.
  • FIG. 2 shows a state in which m is 8.
  • the valve plate 14 is constructed and arranged such that the cylinder fluid chambers 18 associated with those pistons 3 which are in the state inwhich they are pushed and moved outwardly of the cylinder body 2 by the working fluid communicated through the ducts with the fluid passageway 21 on the higher pressure side, and that the cylinder fluid chambers 18 associated with those pistons 3 which are in the' state in which they are pushed and moved inwardly of the cylinder body 2 by the working fluid communicated through the ducts 16 with the fluid passageway 22 on the lower pressure side or discharge side.
  • cams 6 mounted on the pinion shafts 4 have an outer diameter which is equal to the diameter of the pitch circle of the pinions 5, then the pinions move in rolling motion while being maintained in meshing engagement with the internally toothed gear 9, add no slip occurs between the cams 6 and ring rests 7 when the cams 6 move in rolling motion along the inner peripheral surfaces of the ring rests 7, thereby permitting the cams 6 to be maintained in rolling contact with the ring rests 7.
  • the device according to this invention is adapted for operation with a high pressure working fluid. Besides, the device can withstand high speed operation because centrifugal forces exerted by the pinions 5 are borne by the associated ring rests 7.
  • a spring may be provided in each piston for facilitating the actuation of pistons during the suction stroke of the pump.
  • the pinions 32 are maintained in meshing engagement with the external gears 36 as contrasted to the pinions being maintained in meshing engagement with the internally toothed gear 9 in the first embodiment. Consequently, the cams or rolling rings 33 moves in rolling motion along the inner surfaces of the ring rests 34. Since the piston pin 30 is eccentric with respect to the pinion shafts 31, the piston 29 can be moved in reciprocating motion.
  • cams 6 of the embodiments which are adapted to be maintained in engagement with the ring rests 7 have been explained with reference to an example in which the cams 6 are in the form of eccentric rings. It is to be understood, however, that any shape as desired may be selected for the cams 6, note FIGS. 14 and 15 where the cam 6 and the pinion 5 are egg-shaped, so long as the shape satisfies the characteristics required of a fluid device.
  • FIG. 6 A shows the relation between the angle of rotation 0 of the main shaft 1 and the torques produced by the pistons (which are required torques in the case of a fluid pump, hereinafter to be referred to as produced torques) when the cams 6 are eccentric rings or eccentric cams.
  • the angles of rotation of the main shaft are set forth along the axis of abscissa and the produced torques along the axis of ordinates.
  • a piston which may be called a first piston
  • a second piston which is a piston operating next to the first piston in chronological sequence and which need not necessarily be a position disposed adjacent the first piston
  • a torque which can be represented by a sine curve formed by connecting points 42, 44 and 45 together.
  • the fluid motor provided with these pistons will produce torque which can be represented by a composite curve which can be formed by connecting point 46, 47, 48 and 49 together as shown in FIG. 6 B which is obtained by combining the sine curves representing the torques produced by all the pistons. It will be seen that this composite curve has highly elevated portions and highly depressed portions, indicating that the produced torques exhibit great changes in value.
  • a first piston will produce a torque which can be represented by a curve formed by connecting points 50, 52 53 and 51 together
  • a second piston will produce a torque which can be represented by a curve formed by connecting points 54, 56, 57 and together. It will be seen that a portion of the torque produced by the first piston between the points 52 and 53 and a portion of the torque produced by the second piston between the points 56 and 57 are equal to each other, and that the time intervals during which the torques are produced by the first piston and second piston between the points 53 and 51 and the points 54 and 56 respectively overlap each other.
  • a curve representing the composite torque obtained by combining the torque produced by the first piston and the torque produced by the second piston will be represented by a straight line as shown in FIG. 6 D, indicating that there is no change in the values of torques produced by the pistons.
  • FIG. 6 E shows an example in which the torques produced by the pistons undergo changes that can be expressed linearly.
  • changes in the torques produced by the pistons are defined such that the composite curve of the produced torques can be expressed as a straight line in the same manner as the case shown in FIG. C.
  • time interval 60, 64 (corresponding to the distance between the points 60 and 64) during which the second piston lags behind the first piston in being actuated is one-half the time interval 60, 61 (corresponding to the distance between the points 60 and 61), it will be impossible to bring the first and second pistons into corrected relationship unless the torques produced by the first and second pistons are made to undergo changes which are triangular in shape as shown in FIG. 7
  • changes in the torque produced by the first piston are expressed by a curve formed by connecting points 91, 93, 94 and 92 together, changes in the torque produced by the second piston by a curve formed by connecting points 95, 96, 93 and 97 together, changes in the torque produced by the third piston by a curve formed by connecting points 98, 99, 96 and 100 together, changes in the torque produced by the fourth piston by a curve formed by connecting points 101, 102, 99 and 103, and changes in the torque produced by the fifth piston by a curve formed by connecting points 104, 105, 102 and 106 together.
  • the first piston in the former half of the produced torque curve is in corrected relationship with the third, fourth and fifth pistons.
  • the sums of yalge 91, 93 and the values 96, 100, 99, 103, and 102, 106 at each point in time or at the same rotational angle are constant as shown in FIG. 8 B.
  • the pistons showing changes represented by lines 103, 107, 100, 108 and 97, 109 are in corrected relationship with the first piston represented by the line 94, 92, so that the sums of the values at each point in time are constant as shown in FIG. 8 B.
  • the pistons can be brought into corrected relationship with one another even if the former half and the latter half of the wave form of a curve representing the torques produced by the pistons are not symmetrical.
  • FIG. 9 shows the relation between the rotational angle 6 of the main shaft 1 and the stroke S of a piston in a case in which the ring cams 6 are eccentric rings.
  • the rotational angle 6 of the main shaft is plotted as the axis of abscissa against the piston stroke S as the axis of ordinates.
  • a given piston (which may be a first piston) moves in a piston stroke represented by a sine curve formed by connecting points 120, 121, 122 and 123.
  • the points 121 and 123 are upper dead points and the point 122 is the lower dead point of the piston stroke.
  • Points 124 and 125 and 126 are points at which fluid passageway 17 to the cylinder fluid chamber 18 is switched from communication with one of the ducts 15 to communication with one of the ducts 16 or vice versa.
  • the piston moves in force-in operation from the upper dead point to the lower dead point between the points 124 and 125 so that the operation fluid in the cylinder fluid chamber 18 is discharged through one of the ducts 16.
  • the piston moves in forceout operation from the lower dead point to the upper dead point between the points 125 and 126, so that the operation fluid is supplied to the cylinder fluid chamber 18 through one of the ducts 15.
  • piston operation follows a curve formed by connecting points 127, 134, 128, 135, 136, 129, 137, 138, and 139.
  • the points 128 and 130 are the upper dead points and the point 129 is the lower dead point, and the points 131, 132 and 133 are points at which switching between the ducts of valve plate is effected.
  • the sections in which the piston stroke speed is zero are formed between the points 134 and 135 with the lower dead point 129 being disposed at its center, between the points 136 and 137 with the lower dead point 130 being disposed at its center, and between the points 138 and 139 with the upper dead point 130 being disposed at its center.
  • Piston operation can be performed as planned to achieve desired results if the deviation of the upper and lower dead points from indexing with the switch points is within the range of each of such sections. Besides unnecessary piston movement can be prevented and occurrence of noises and vibrations can be precluded.
  • this invention makes it possible to obtain a fluid device, simple in construction and easy to manufacture because no close tolerances need be maintained, which can be adapted as a pump or a motor for handling a fluid of high pressure at high speed.
  • the first embodiment shown and described herein operates such that the main shaft can be connected to an input shaft or output shaft, and the internally toothed gear is firmly fixed, the main shaft can be firmly fixed and the internally toothed gear can be connected to as an input shaft or output shaft.
  • gear according to this invention makes it possible to provide a fluid device which is less complex in construction and easier to manufacture than conventional fluid devices in which pistons are made to move in sliding motion on a complicated cam surface.
  • a fluid device for use as a radial piston pump or motor comprising a casing, a main shaft rotatably supported in said casing, a cylinder body mounted on said main shaft and held against rotation relative thereto, a plurality of pistons in said cylinder body arranged radially thereof and spaced apart in an annular arrangement about said main shaft for reciprocating motion, said pistons arranged to operate in pairs with said pistons in each said pair spaced apart in the axial direction of said main shaft, pinion means operatively associated with each said pair of pistons and said pinion means in cluding a pinion shaft extending in parallel relation with said main shaft, a piston pin eccentrically positioned in said pinion shaft and mounted at opposite ends to said pistons in one said pair of pistons, and a pinion gear concentrically mounted on said pinion shaft, a casing gear fixed to said casing, said pinion gear disposed in meshed engagement with said casing gear so that reciprocation of said pistons and rotary displacement of said eccentric pins effects relative rotary motion between
  • a fluid device according to claim 1 wherein said cam means is formed in the shape of a ring.
  • a fluid device according to claim 1 wherein said casing gear has integral teeth.
  • a fluid device including hearing means rotatably supporting said cam means on said pinion means.
  • a fluid device according to claim 1 wherein said engaging means comprises a ring rest element fixed to said casing.
  • a fluid device according to claim 1 wherein said eccentric pins extend from each longitudinal end of said body portion of said pinion means, said pinion gear being located on said body portion of said pinion means.
  • a fluid device according to claim 1 wherein said body portion of said pinion means has two parts, one each disposed at the longitudinal ends of said eccentric pin, each of said body portion parts carrying a pinion gear.
  • cam means has a configuration operable to cause two or more pistons to effect coordinated operating strokes so that the sum of the torques produced by said pistons is maintained constant during operation of the fluid device.
  • a fluid device according to claim 1 wherein said cam means has a configuration operable to cause said piston to remain at top dead center and bottom dead center for predetermined angles of relative rotary displacement between said main shaft and said casing.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Valve Device For Special Equipments (AREA)
US00174097A 1970-08-25 1971-08-23 Fluid device Expired - Lifetime US3827338A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP7385070 1970-08-25

Publications (1)

Publication Number Publication Date
US3827338A true US3827338A (en) 1974-08-06

Family

ID=13530020

Family Applications (1)

Application Number Title Priority Date Filing Date
US00174097A Expired - Lifetime US3827338A (en) 1970-08-25 1971-08-23 Fluid device

Country Status (6)

Country Link
US (1) US3827338A (enrdf_load_stackoverflow)
DE (1) DE2142323B2 (enrdf_load_stackoverflow)
FR (1) FR2106028A5 (enrdf_load_stackoverflow)
GB (1) GB1347332A (enrdf_load_stackoverflow)
NO (1) NO138225C (enrdf_load_stackoverflow)
SE (1) SE379830B (enrdf_load_stackoverflow)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3924516A (en) * 1972-07-06 1975-12-09 Deere & Co Hydraulic pump or motor
WO1988000639A1 (en) * 1986-07-23 1988-01-28 Sea Shelf Engineering Pty Ltd. A hydrocyclic motor
US20080206073A1 (en) * 2005-04-15 2008-08-28 Niall James Caldwell Fluid-Working Machines
US20160123311A1 (en) * 2013-06-18 2016-05-05 Artemis Intelligent Power Ltd. Fluid working machine
US20240044319A1 (en) * 2020-12-16 2024-02-08 Danfoss Power Solutions (Jiangsu) Co. Ltd. Hydrostatic radial piston unit
US20240328381A1 (en) * 2021-12-16 2024-10-03 Danfoss Power Solutions (Jiangsu) Co., Ltd. Brake mechanism for a radial piston unit

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US593470A (en) * 1896-05-05 1897-11-09 Island
US668855A (en) * 1898-12-05 1901-02-26 John F W Koetter Motor.
US797571A (en) * 1901-10-31 1905-08-22 Frank C Goddard Explosive-engine for motor-vehicles.
US1004504A (en) * 1910-07-06 1911-09-26 Luther Van Nette Vacuum-cleaner.
US2010378A (en) * 1931-07-28 1935-08-06 Cincinnati Milling Machine Co Hydraulic power unit
US2303685A (en) * 1940-05-11 1942-12-01 Eden Charles Howard Hydraulic transmission
US2416940A (en) * 1945-04-13 1947-03-04 James E Morton Fluid pressure motor
US2712794A (en) * 1949-06-15 1955-07-12 Marion W Humphreys Fluid motor or pump
US3046950A (en) * 1958-01-22 1962-07-31 Whiting Corp Constant mechanical advantage rotary hydraulic device
US3331326A (en) * 1965-05-26 1967-07-18 Leonard R Casey Rotary pump
US3656405A (en) * 1969-11-11 1972-04-18 Dickertmann Hebezeugfab Ag Pressurized medium motor
US3661057A (en) * 1970-05-11 1972-05-09 Anatoly Yakovlevich Rogov Radial-piston multiple-action hydraulic motor

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US593470A (en) * 1896-05-05 1897-11-09 Island
US668855A (en) * 1898-12-05 1901-02-26 John F W Koetter Motor.
US797571A (en) * 1901-10-31 1905-08-22 Frank C Goddard Explosive-engine for motor-vehicles.
US1004504A (en) * 1910-07-06 1911-09-26 Luther Van Nette Vacuum-cleaner.
US2010378A (en) * 1931-07-28 1935-08-06 Cincinnati Milling Machine Co Hydraulic power unit
US2303685A (en) * 1940-05-11 1942-12-01 Eden Charles Howard Hydraulic transmission
US2416940A (en) * 1945-04-13 1947-03-04 James E Morton Fluid pressure motor
US2712794A (en) * 1949-06-15 1955-07-12 Marion W Humphreys Fluid motor or pump
US3046950A (en) * 1958-01-22 1962-07-31 Whiting Corp Constant mechanical advantage rotary hydraulic device
US3331326A (en) * 1965-05-26 1967-07-18 Leonard R Casey Rotary pump
US3656405A (en) * 1969-11-11 1972-04-18 Dickertmann Hebezeugfab Ag Pressurized medium motor
US3661057A (en) * 1970-05-11 1972-05-09 Anatoly Yakovlevich Rogov Radial-piston multiple-action hydraulic motor

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3924516A (en) * 1972-07-06 1975-12-09 Deere & Co Hydraulic pump or motor
WO1988000639A1 (en) * 1986-07-23 1988-01-28 Sea Shelf Engineering Pty Ltd. A hydrocyclic motor
US4974496A (en) * 1986-07-23 1990-12-04 Sea Shelf Engineering Pty. Ltd. A hydrocyclic motor
US20080206073A1 (en) * 2005-04-15 2008-08-28 Niall James Caldwell Fluid-Working Machines
US8347778B2 (en) * 2005-04-15 2013-01-08 Artemis Intelligent Power Limited Fluid-working machines
US20160123311A1 (en) * 2013-06-18 2016-05-05 Artemis Intelligent Power Ltd. Fluid working machine
US20160356160A1 (en) 2013-06-18 2016-12-08 Artemis Intelligent Power Ltd. Fluid working machine
US10677058B2 (en) 2013-06-18 2020-06-09 Danfoss Power Solutions Gmbh & Co. Ohg Fluid working machine having offset valve cylinders
US10995739B2 (en) * 2013-06-18 2021-05-04 Danfoss Power Solutions Gmbh & Co. Ohg Fluid working machine having first and second valve cylinder devices in fluid communication with each other via a common conduit
US20240044319A1 (en) * 2020-12-16 2024-02-08 Danfoss Power Solutions (Jiangsu) Co. Ltd. Hydrostatic radial piston unit
US20240328381A1 (en) * 2021-12-16 2024-10-03 Danfoss Power Solutions (Jiangsu) Co., Ltd. Brake mechanism for a radial piston unit

Also Published As

Publication number Publication date
FR2106028A5 (enrdf_load_stackoverflow) 1972-04-28
GB1347332A (en) 1974-02-27
SE379830B (enrdf_load_stackoverflow) 1975-10-20
DE2142323A1 (de) 1972-03-09
NO138225B (no) 1978-04-17
DE2142323B2 (de) 1978-02-23
DE2142323C3 (enrdf_load_stackoverflow) 1978-10-19
NO138225C (no) 1978-08-02

Similar Documents

Publication Publication Date Title
US2871831A (en) Internal gear machines
US3396632A (en) Volumetric maching suitable for operation as pump, engine, or motor pump
US3490383A (en) Hydraulic pump or motor
US2484789A (en) Variable displacement pump and motor
US3833317A (en) Rotary gear motor/pump having hydrostatic bearing means
US1989552A (en) Rotary compressor
US3654761A (en) Fluid handling device with radially variable working chambers
US2240874A (en) Rotary fluid-pressure machine
US3827338A (en) Fluid device
US3597128A (en) Hydraulic device having hydraulically balanced commutation
US3547565A (en) Rotary device
US3910732A (en) Gerotor pump or motor
US3699848A (en) Radial piston fluid pressure motor
US3474954A (en) Rotary volumetric machine
US2453271A (en) Rotary alternating pistons pump
US1455443A (en) Balanced hydraulic pump or motor
US2694978A (en) Rotary power device of the rotary abutment type
US3796525A (en) Energy translation devices
US3723031A (en) Rotary displacement machines
EP0033544B1 (en) Internal-axis gear-type fluid machine with distribution means
US2416940A (en) Fluid pressure motor
US2070738A (en) Pump with cam drive
US3187677A (en) Rotary piston pump
US3056355A (en) Hydraulic apparatus
US2993339A (en) Rotary, hydraulic pump and motor transmission